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(No Medal.) 4 Sheets-Sheet 1.

O. P. HOLST. PUMP AND MECHANISM FOR OPERATING SAME.

No. 593,099. Patented Nov. 2, 1897.

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(No Model.) 4 Sheets-Sheet 2.

C. P. HOLST. PUMP KND MECHANISM FOR OPERATING SAME.

No. 593,099. Patented Nov. 2, 1897.

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4 Sheets-Sheet s.

(No Model.)

0. P. HOLST. V PUMP AND MECHANISM FOR OPERATING SAME. No.v593,099.

Patented Nov. 2, 1897.

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PUMP AND MECHANISM FOR ()PERATING SAME. No. 593,099. Patented Nov. 2, 1897.

UNITED STATES Arena rarer...

CONSTANTYN PIETER I'IOLST, OF AMSTERDAM,- NETHERLANDS.

PUMP AND MECHANISM FOR OPERATlNG SAME- SPECIFICATION forming part of Letters Patent No. 593,099, dated November 2, 1897.

Application filed November 20, 1895. Serial No. 669,524. (No model.) Patented in England September 20, 1894, No. 17,883. v

To (tZZ whom it may concern:

Be it known that I, CONSTANTYN PIETER HoLs'r, Gzoon, engineer, a subject of the Queen of the Netherlands, residing in Amsterdam, Netherlands, have invented new and useful Improvements in Pumps and Mechanism for Operating the Same, (for which I have obtainedapatentin Great Britain, No. 17,883, dated September 20, 1894,) of which the following is a specification.

My invention is designed to render it possible to employ high rates of speed of the pump-buckets or of the actuating crank-shaft in the operation of reciprocating pumps while insuring the movement of the liquid at a constant or uniform velocity and in an uninterrupted stream.

In the accompanying drawings my improved pumping apparatus is illustrated, by way of example, in several forms.

Figures 1 and 2 are respectively a side elevation and asectional plan or top View, representing a quadruple bucket pump constructed in accordance with my invention coupled to and immediately adjoining a driving-engine comprising two cylinders, such as a compound engine. Fig. 3 is a side elevation, partly in vertical section, and Fig. 4.- an end elevation, representing a triple-bucket pump constructed according to my said invention. Figs. 5 and 6 are diagrams illustrating the working of the equalizing mechanism shown in Figs. 1 and 2 and in Figs. 3 and 4, respectively, forimpartingmotion from the crank-shaft to the buckets in such a man ner that the velocity of each bucket will first gradually increase, then remain constant or uniform throughout the whole of the eflective part of its stroke, and will then gradually diminish until the said bucket comes to rest at the termination of its stroke. Fig. '7 is a longitudinal central section, drawn to an enlarged scale, illustrating details of construc-" tion.

My invention relates to multiplebucket pumping-engines of the kind or class wherein the pump cylinders or chambers are connected up to form a single continuous curved line or series and the valves of the valved pistons or buckets all open in the direction of flow of the fluid, and in which reciprocating motion is imparted to the said buckets in such a manner that each bucket in turn will, during a portion of its stroke in the direction of flow of the fluid, move at a higher velocity than the other bucket or buckets moving in the same direction as the liquid flowing through them, and will consequently have its valve closed and will drive the fluid forward, while all the other buckets have their valves open, so as to allow the fluid to pass through them. In pumping apparatus of this kind or class, if the differences of phase between the motions of successive bucketsthat is to say, successive in the continuous line of flowbe equal and the number of buckets be such that these differences of phase together make up a complete period, then the several buckets will successively drive forward the fluid as they successively attain the required higher velocity in the direction of flow. For example, the first bucket, as soon as it begins to move at a higher velocity than the other buckets moving in the same direction as the liquid flowing through them, will drive the fluid forward until its velocity becomes less than that of the next bucket,which in its turn will attain a higher velocity and drive the fluid forward until its velocity decreases below that of the third bucket, which will in its turn drive forward the fluid, and so on until the completion of the cycle or period of motion, when the said operations will be repeated. The length of the effective portion of the stroke of each particular bucket is, therefore, that portion thereof during which it moves faster than the other buckets moving in the same direction as the fluid flowing through them. In order, however, that the velocity of the fluid shall be constant or uniform, it is necessary to impart reciprocating motion to the buckets in such a manner that the velocity of each of them shall be constant or uniform during the whole of the effective portion of its stroke, and thus a continuous and uniform force will at all times be exerted to draw in and discharge the fluid and cause the same to flow in a continuous and unvarying stream through the pumping apparatus. The main object of my said invention is to accomplish this result.

To this end my invention consists in the novel combination of parts hereinafter set forth and claimed.

In Figs. 1, 2, and 5 I have shown one form of my pumping apparatus in which four buckets I II III IV are arranged in cylinders a a a a and are mounted in pairs on rods bb', driven by means of a two-cylinder engine having its cranks set at an angle of ninety degrees to each other. The buckets I and III are mounted on the rod 7), driven by the crank P, and are so arranged that their valves open in opposite directions. The buckets II and IV are mounted on the rod b, driven by the crank R, and their valves also open in opposite directions. The said cylinders a a a a are connected with each other and with the inlet and delivery apertures M and N in a continuous series by means of pipes H K L in such a manner that the valves of the several buckets will all open in the same direction as that in whichthe fluid flows through the corresponding cylinders.

Between the end E of each pump-rod and the end A of the taihrod c of the corresponding engine-piston is arranged a set of equaL izin'g mechanism so constructed and arranged that each bucket will be caused to travel at a constant or uniform maximum velocity, while the corresponding crank -is moving through one-fourth of its revolution-that is to say, through the median arc of ninety degrees in the backward or the forward stroke of the corresponding engine-piston. In this manner the motion of each piston in both the.

backwardand the forward direction is utilized for driving the fluid forward through the pumpingapp'aratus, the continuous motion of the fluid being obtained by arranging the cranks P R at an angle of ninety degrees to each other, so that there is always one or another of the buckets moving at its maximum velocity in the same direction as the fluid, the cycle of operations being as hereinafter describedthat is to say, following the shaft provided with the crank P B through one revolotion, and assuming the crank R to be starting from 0 in the crank circle in Fig. 5, first, the crank R passes effectively from 0 to 8, while the crank P passes ineffectively from g too, and the bucket II drives forward the liquid; second, the crank R passes ineffectively from S to 1), while the crank P passes effectively from 0 8, and the bucket III acts in its turn upon the liquid; third, the crank B passes effectively from p to q, while the crank P passes i'neffectively from 8 to p, the bucket IV acting upon the liquid; fourth, the crank R passes ineffectively from g to 0, while the crank P passes effectively from pto q, and

the bucket I acts to drive forward the liquid.

The above cycle of operations is repeated in each revolution of the crank-shaft. In this case there are four change-over points in the revolution of the crank-shaftviz., 0, 8, p, and q, and it will be seen that as soon as the rate of speed of one bucket begins to diminishfrom its maximum the next bucket attainsits maximum rate of speed. The liquid is therefore driven forward uninterruptedly and uniformly.

In Figs. 3, 4, and 6 I have shown another form of my improved pumping-apparatus in which three pump-cylinders a a a are arranged parallel with each other and are connected in a continuous series by means of pipes H K, so as to form a continuous passage for the fluid. In each of these cylinders works a pump-bucket I, which is driven from a separate crank O, the cranks being set at an angle of one hundred and twenty degrees to each other and the said crank-shaft being driven in any suitable manner.

Each bucket I is connected to the correspondin g crank-pin by a separate set of equalizing mechanism, whereby the corresponding pump-bucket will be moved at a constant or uniform maximum velocity during one-third of the revolution of the crank-shaft. This part of the revolution of each crank is the are 0 to 8, Fig. 6. Therefore as each crank enters this are the corresponding bucket will be the acting or propulsive bucket, and since one of the cranks must always be within this are it follows that the fluid will always be driven forward by one or other of the buck ets at a constant or uniform velocity.

The equalizing mechanism in each case consists of a triangular link A B 0, which has one of its angular points A connected directly to the driving part (in the one case the tail-rod c of the engine-pistonand in the other case the crank-pin) and its angular point B connected by means of a link D or D to the end E of the plunger rod of the correspondingbucket,the remainingangular point C of the said triangular link being coupled toa swinging or rocking bar F, turning about a fixed pivot G, whereby its motion is controlled so that it must move in an arc of a circle having as its center the pivot or axis G. The action of this mechanism in equalizing the motion transmitted from the crankshaft to the buckets, respectively, during the effective portion of the stroke thereof may be described, in general terms, to be substantially as follows;

Referring to Figs. 1, 2, and 5 and assuming that the crank P is starting from the point (1, the angle passed through by the said crank between q and 0 in the direction indicated by the arrow is that in which the ratio of travel of the bucket to angular motion of the crank is low, and this part of the motion is ineffective, the liquid during such movement of the crank P being driven forward by the bucket II actuated by the crank B. When the crank P arrives at the point 0 in the crank circle, the triangular link A B O occupies the position shown in Fig. 5. In the movement of the said crank P from 0 to 2 the motion of the points A and E is accelerated by means of the triangular link A B 0, controlled by the rocking bar F, so as to bring the velocity of the point E up to its maximum value. From the point 2 to 6 the motion of the said points A and E is retarded by the said link under the control of the rocking bar, and from 6 to 8 such motion is again accelerated, so that during the movement of the crank P from o to 8 the velocity of the corresponding bucket has a constant or uniform maximum value, notwithstanding the angular motion of the crank.

Referring to Figs. 3, 4, and 6 and starting from the point a, the angle first passed through by the crank between a. and 0 corresponds to the part of the travel where the ratio of distance passed over by the pointE to angle de scribed by the crank has its minimum values. This portion of the stroke is, therefore, not employed for propulsive purposes. As the crank-pin passes between the points 0 to 2 the motion of the points A and E is accelerated by the swinging of the triangular link A B 0 about its suspension G, so as to bring the veiocity of the said point E up to its maximum value. As the crank passes from 2 to 6 the swinging of the triangular link A B G acts to retard the motion of the points A and E, and thus keep' the velocity of the said point E down at its maximum value. While the said crank is passing from 6 to 8, the motion of E is again accelerated, while the remaining angles 8 to Z2 and I) to a, completing the travel, are not employed for propulsive purposes. Therefore d uring the movement of each crank in turn from the point 0 to 8 the velocity of the corresponding bucket will have a constant or uniform maximum value notwithstanding the angular motion of the crank.

In Figs. 5 and 6 the relative positions of the points A, B, G, and E, when the crank is at the points 0 to 8, respectively, are indicated by corresponding figures.

The construction and arrangement of the intermediate equalizing mechanism will be varied according to the desired ratio of velocity of the pump-buckets to the mean velocity of the engine-pistons.

The form or construction of bucket which I prefer to employ, so as to maintain the cross-sectional area of the fluid-column constant, is shown more clearly in section in Fig. 7 with its valve V closed, the. dotted lines showing the position of the said valve when open. The valve V is provided witha guide-sleeve V, which slides on a cylindrical part W'of the bucket, and is adapted to rest against a shoulder W on the said bucket when the valve is open. In order that the said valve may rapidly close when or immediately before the said bucket attains its maximum velocity, holes are formed through the part IV, so that the liquid can pass to the back of the valve and prevent the formation When the valve is open, the

of a vacuum.

water passes on both the inner and outer 6o 1. In an apparatus for pumping fluids, the

combination of pump-cylinders arranged in a continuous series, reciprocating valved pistons or buckets therein, interconnected cranks for driving said buckets, and intermediate equalizing mechanism between each of said cranks and the corresponding bucket or buckets, comprising a triangular lever one point of which moves through an arc of a circle, another point being connected to the corresponding crank, while its third point is connected to the pump-rod or plunger-rod,and whereby each bucket in turn is caused to move at a constant or uniform maximum velocity during the whole of the effective portion of its stroke, substantially as, and for the purposes, hereinafter described.

2. The combination of the pump-cylinders arranged in a continuous series, reciprocating valved pistons or buckets therein, interconnected cranks for driving said buckets, and triangular links each having oneof its an gularpoint-s connected with the corresponding crank, and another of such points connected with the corresponding bucket, and a swinging or rocking bar mounted 011 a fixed pivot and coupled at its free end to the third angular point of said triangular link, substantially as, and for the purposes, above specified.

3. The combination of pump-cylinders arranged in a continuous series, reciprocating buckets therein having enlarged plungers and annular valves with cylindrical guidesleeves, and having their valve-openings approximately equal in cross-sectional area to the annular spaces between said enlarged plungers and the pump-cylinders, interconnected cranks for driving said buckets, and

IIO

intermediate speed-eqnalizing mechanism between each of said cranks and the corresponding bucket or buckets, substantially as, and for the purposes, hereinbefore described.

CONSTANTYN IIE'lER HOLS'I. WVitn esses:

THOMAS HERMANN VERHAVE, Aueusr Srnernrnn DOCH. 

